Automatic press for extracting oil from seed-meal.



H. A. HERB. AUTOMATIC PRESS FOR. EXTRAGTING OIL PROM SEED MEAL.

APPLICATION FILED 1611170151904. 968,153, Patented A11 23, 1910.-

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H. A. HERB. AUTOMATIC PRESS FOR EXTRAGTING OIL FROM SEED MEAL.

APPLICATION FILED MAB. I5, 1904.

Patented Aug.23, 1910.

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APPLICATION FILED MAR. 15, 1904.

Patented Aug. 23, 1910.

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H. A. HERR. AUTOMATIC EEEss EoE EXTRAGTING OIL FROM SEED MEAL.

APPLICATION FILED MAR. 16, 1904. Patented 1o SHEETS-SHEET 4.

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Patented Aug. 23,4910.

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AUTOMATIG PRESS FOR EXTRAGTING OIL PROM SEED MEAL. APPLIUATION FILED MAR. 15, 1904.

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-H. A. HERB. AUTOMATIC PRESS FOR EXTBAGTING OIL. FROM SEED MEAL.

APPLICATION IILBD KAB. 15, 1904.

Patented Aug. 23, 1910.

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THE NORRIS PETERS co, wAsmmznm, n, c.

H. A. HERE. I AUTOMATIG PRESS FOB EXTBAGTING OIL FROM SEED MEAL.

APPLICATION IILBD MAR. 15, 1904. 968,1 53. Patented Aug. 23, 1910.

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H. A. HERE. AUTOMATIC PRESS FOR EXTRAGTING OIL FROM SEED MEAL. APPLIOATION FILED MAR. 15, 1904.

968, 1 53, Patented Aug. 23. 1910.

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H. A. HERB. AUTOMATIC PRESS FOB-EXTRACTING OIL FROM SEED MEAL.

APPLIOATION IILED MAR. 15 1904. 968, 1 5 3 I Patented Aug. 23, 1910.

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H. A. HERR. AUTOMATIC PRESS FOR EXTRAGTING OIL FROM SEED MEAL.

APPLICATION FILED MAR. I5 1904.

' Patented Aug. 23, 1910.

10 SHEETS-SHEET 10.

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HOMER A. HERR, OF PHILADELPHIA, PENNSYLVANIA.

AUTOMATIC PRESS FOR EXTRACTING- OIL FROM SEED-MEAL.

Specification of Letters Patent.

Patented Aug. 23, 1910.

Application filed March 15, 1904. Serial No. 198,259.

I '0 all whom it may concern:

Be it known that I, HOMER A. HERR, a citizen of the United States, residing at Philadelphia, in the county of Philadelphia and State of Pennsylvania, have invented certain new and useful Improvements in Automatic Presses for Extracting Oil from Seed-Meal, of which the following is a specification.

My invention has reference to automatic liquid extracting presses and consists of features fully set forth in the following specification and the accompanying drawing forming part thereof.

WVhile it relates to liquid extracting presses, my present invention has reference more particularly to the expressing of oil from seeds, such as cotton seed, fiaxseed and other seeds requiring a heated condition of the meal while under pressure.

In my application filed Nov. 6th, 1902, No. 130,239 and Oct. 6th, 1903, No. 176,020 I show an automatic liquid extracting press. That is the feeding of the material into the press, the starting of the pressure, the stopping of the pressure, the sustaining of the pressure for a predetermined time, the predetermining of this time, the returning of the elements to their normal position, the opening and the closing of the bottom of the compression chamber and the discharging of the residuum from the said chamber while open: all of which functions are automatic.

This present invention includes the automatic features above enumerated, but is an improvement thereon in the specific arts stated, 2'. 6.. vegetable oils or seed oils. It is well known that .oil will not flow readily unless at a certain heated condition and the present presses must be operated almost one half of .a day before they are in condition of heat to permit the free flow of the oil. This entails a great waste of oil. I heat my oil compression chamber and this obviates all the useless waste now such a universal source of loss to the oil mills.

The present practice in the extraction of oil from seed meal is to first grind the seed to a fine flour, heat it and form it into cakes as a matter of convenience in the handling then wrap this cake wit-h a cloth which will perform the function of strainer, after which the cake, so wrapped, is put into the press, one cake on the top of another until the press is full, after which the pressure is applied by the turning on of the water either by the starting of a pump or the opening of a valve leading to an accumu lator. All these different operations require labor and make the margin of profit exceedingly small in the oil mill. They not only require labor but exceeding care in some of the essential functions. My invention obviates all this labor and makes what has been heretofore considered an impossibility: an automatic and practical oil mill.

It consists, in combination with the features above set out of a steam jacketed movable lid for the chamber wherein the comression is accomplished; also heated sides or this chamber. The heat can be produced by any means, steam, hot Water, electricity or any of the well known means for heat generation. Above the lid is the meal warmer and meal cooker. Above the cooker is the supply of meal, fed to the said cooker by a conveyer from the rollers of the grinding machine (not shown).

A further feature of my present machine is to supply a knife on the forward moving end of the lid, a highly useful element in an automatic machine of this class. This knife can be made in any manner that will accomplish the object of its design, which is to facilitate the passage of the lid through the material to be pressed, and to cut through any material which by its abnormal resistance to the slowly moving lid may possibly injure the machine, or some of its lid propelling elements. These knives should in some cases be made reciprocating, in such arts as fish oil extraction and the expressing of oil from meat scraps, for instance.

A further feature of my invention is to provide a safety gate for the lid in the vent of any substance being caught or retained in the material that the knife will not cut. This gate consists of a spring controlled wing carried by the compression chamber which wing will yield on pressure being exerted thereon by some foreign object being by accident left in the material in the chamber. In the absence of this safety gate the interposition of such material would break'the machine. This prevents such accidents absolutely.

In my application filed Oct. 6 1903, above referred to I show a sustainer for high maximum pressure fixed to and ,coacting I plied limitations of this term.

with an individual pump. The design in that application being to use one sustainer or one high pressure sustaining device to each pump and one pump to each press.

A further feature of my present invention is to provide a fixed high pressure sustainer for each of a series of presses and a common pump or a common accumulator, whereby the pump is continuous in its action and the accumulator constant and uniform in its pressure, in so far as the connection between the accumulator and the hydraulic cylinders are concerned. Of course the pressure in the hydraulic cylinder when it is operated by an accumulator is not the same as is the pressure in the liquid conductor leading from the accumulator to the said cylinder, until the said cylinder is forced up to gage of pressure. Now while I speak of a series of presses in combination with a common pump or an accumulator I of course do not mean that this feature of my invention cannot be used with a single pump, or with a single accumulator and single pump combined, or indeed without any accumulator at all. I do not limit myself in this regard and my desire will be pointed out in the claims.

It may be well at this time to note that I regard the pump and the accumulator as equivalents for the purpose of my invention. The admission of water into the hydraulic cylinder furnishes the power for producing the pressure on the ram. Now when my presses are arranged in series the opening of a valve admits this water from the pressure in the accumulator; when, however, a single press is used it is admitted directly from the pump without the intervention of the accumulator. I, therefore, desire it understood that I consider the opening of the valve of my pressure sustaining device, which admits the water from the accumulator, as an equivalent to the starting of the fast pulley on the pump. In either case the cylinder and the ram it carries are brought under the action of compressed water through the automatic means furnished in and by my pressure sustainer. While I may file specific individual applications later to cover these features specifically, in this present case I claim broadly the means for automatically controlling the pressure in a series of presses by liquid compression either from the pump, or through the accumulator and either through the respective cylinders as intermediate conductors of the liquid from the pump or accumulator to their respective pressure controllers or otherwise. I also desire it understood that when I use the term belt shifter I do not limit myself to the im- There are many other ways in which power and motion can be shifted than by a belt. All old. I could use a friction clutch, a aw clutch or an electrical armature, I place no restrictions on my resources in this regard. They are all equivalents. The specific naming of them is not essential.

A still further feature of my present invention is to provide the mechanism which actuates the lid and bottom with a means to absolutely insure its locking contact at every degree of the circle of the clutch on the shaft which carries it. The rotation of this clutch is strictly the cycle of the machine. This consists of providing a key fixed to the shaft and having a longitudinal slot in the clutch in which this key moves with an enlarged annular cross section, in other words wider than the accommodation of the key calls for. Two springs are carried by the moving part of the clutch. These springs operate compression fingers, an adjusting screw forces the springs against the fingers adjustably and hold the fingers against the key in the shaft. Now as the springs are of like power the pressure on either side of the said key is uniform and, therefore, the clutch is held with the key in the center of the enlarged longitudinal slot. The clutch will, therefore, rotate to the right or to the left of its normal position on the shaft, compressing the right or the left spring and engaging the jaws at all times, as will be more fully described more at length hereinafter.

A still further feature of my invention is to provide each press, whether used singly or in series, with a device for holding the pressure in case of leakage of valves or fittings. This consists of a valve chamber which carries an exhaust valve for exhausting the water from the cylinders and the high pressure pipes and fittings. An accumulator is connected directly with the cylinder. As the accumulator is raised to a predetermined point it strikes a weighted belt shifter. The belt is to be considered as normally on the fast pulley and this accumulator raises and shifts the belt by so doing, the said belt is shifted to the loose pulley. This stops the pump and arrests further pressure. Should leakage exist the said weight of the belt shifter will shift the belt to the fast pulley, thus again pumping up the pressure. If there is no leakage the accumulator will hold the belt on the loose pulley.

In order to exhaust the water from the cylinder and return the pressure to zero and all the pressure producing elements to their normal position, I provide a lock for the accumulator and this lock is actuated by the trip which permits the opening of the exhaust water valve. The accumulator is only locked when a time period for high pressure sustaining has lapsed, and this time period is predetermined by the indicator carried by the pressure sustainer. The accumulator is unlocked by some moving partof the mechanism at about the time the lid of the compression chamber is closed. This lock, is only used when I employ an accumulator, as it is not necessary when I employ a pump alone. These features will be explained more at length hereinafter in connection with the drawings.

Other specific features will be explained more at length hereinafter.

In the drawings like parts are referred to by marks or figures of a corresponding kind in the different views.

Figure l is a side elevation of my machine with a section of the heater and warmer broken away. F ig. 2 is an end view. Fig. 3 is a general plan with the hopper, heater, a portion of the time recorder and pressure sustainer shown and a port-ion removed. Fig. 4 is a transverse section through the machine showing the heater loaded with meal previous to the commencing of a days work. Fig. 5 is a plan of the compression chamber. Fig. 6 is a side elevation of the compression chamber, these two latter views are the parts taken from the machine. Fig. 7 is a front view of the pressure sustainer. Fig. 8 is a horizontal section of the valve chamber. Fig. 9 is a section through the hydraulic cylinder which has its valve shut off by the accumulator of the time recorder, and thus arresting the water feed to the cylinder instead of arresting this feed by the shifting of the belt. Fig. 10 is a view of the valve trip guiding rods removed from the machine. Fig. 11 is an end view of the pressure sustainer mounted on the cylinder. Fig. 12 a section on the line a b (Fig. 10). Figs. 13, 14, 15 and 16 are details illustrating the compensating clutch. Figs. 17 and 18 are details of the meal packing fingers and Figs. 19 and 20 are details as to positions of the meal packing fingers. Fig. 21 is the meal carrying frame. Fig. 22 is a perspective view of one of the meal packers. Figs. 23, 24, 25, 26 and 27 are details of the drainage racks. Fig. 28 shows the cylinders of a series of presses all of different sizes and each having an individual pressure sustainer, all controlled through their respective cylinders by a common accumulator. I omit the indicator from these views. Figs. 29 and 30 are details of the belt reversing means. Fig. 31 is the top of one of the compartments forming the compression chambers. Fig. 32 Sheet5 is a detail of the partition connecting links. Fig. 33 Sheet 5 is a section on line :0 w of Fig. 5. Figs. 34 and 35 Sheet 6 are views of different forms of knives I could use for the lid or top of the compression chamber. Fig.36 Sheet 6 is a vertical section of a portion of the meal warmer and lid of the compression chamber and showing the action of the wing protecting means for the mechanism. Fig. 37 is a side elevation of the belt shifting mechanism. Fig. 38 is a part diagram. 'Fig.

39 is a side view of the belt wheels. Fig. 40 is a detail showing the tripping mechanism. Fig. 41 Sheet 6 is a rear view of the pressure sustained. Fig. 42 Sheet 7 is a vertical sect-ion through the actuating rods for the time trip.

A is the hydraulic cylinder. foundation rest.

C is the ram.

3 is the platen carried by the ram.

4, 4, 4, 4, are a series of partitions form- 1iOng compartments in the compression cham- 1 and l are two plates forming the lateral walls of the compression chamber. At their base these plates are expanded in their relation to each other, thus making the chamber downwardly diverging. The purpose of this divergence is to facilitate the discharge of the oil cake after the oil is extracted from the meal.

2, Fig. 4, not shown in Fig. 1, is a steam jacket on the lateral plates. This is for the purpose of heating the plates and thus the chamber by radiation. These plates are made of heavy steel and must be perfectly smooth on their inner face. This will prevent the adhering to their inner sides of any of the meal cake.

F is the top of the chamber or the lid therefor. It consists of an upper and a lower plate bolted or riveted together and steam tight, forming a steam jacket for the top of the chamber. 5 5 are rollers carried by this lid and they serve as its support. 6 is a link connecting the lever 7 with the said lid, Fig. 4. The said lever is fixed to and operated by the. shaft 8.

H is the warming chamber for the meal. It is jacketed at the one side with a steam chamber as shown in Fig. 4. At the opposite side it is slotted to permit the play of the arms 11. It will be seen the top of the compression chamber F becomes the bottom of the warming chamber. J is the heater proper and the meal is discharged into the said warming chamber after being heated or cooked in the said heating chamber. The

B is its pipe J connects the jacket of the heater J with the jacket of the warmer H. The pipe J connects the jacket 2 of the compression chamber with the jacket of the heater proper.

U, U are a series of plate supports for a series of meal packers V. There are several of these packers on each plate. Best shown in Figs. 17, 18, 19, and 20. These packers pack the meal tightly in the compartments of the compression chamber, one packer for each compartment. My practice takes the place of the cake formers at presentused and I form, so to speak, a series of cakes simultaneously. This packing of the meal insures an even distribution of the meal in the compartments of the compression chamber and therefore an effectual extraction of the oil. As the plate U is raised the packers V, V take the position shown in the dotted lines V, V and the material will pass by them, or they will pass by the material. As they are dropped the packers will spread out and press moderately the meal as shown in Figs. 19 and 20.

Z is the thrust head of the hydraulic press.

D, D are the tension rods.

9, 9 are bolts holding the lateral plates forming the lateral walls of the compression chamber in position against a head former for the chamber 10, Fig. 1 only.

Y, Y are the roller supports for the bottom of the compression chamber. X is a rod on which these rollers are supported and WV the oil or liquid collector carried by the bottom.

E is an oil outlet pipe from the collector leading to the common oil pipe F. The latter of which is the oil conductor of a series of presses, not shown, and leads to the oil reservoir of the oil mill, not shown.

As the plate U, carrying the packers V is raised the arm 11 is also raised. 12 is the shaft which carries the arms 11. The cam 13 of the shaft 131 raises the plate U through the arm 11. Thus the oscillation of the arm 11 packs the compartment of the compression chamber in the manner already described. The pin 15, it will be noted, pivotally holds the packers to the respective plates U.

It is important to have the plates U out of the path of the moving lid F and that they shall operate only when the lid of the chamber is open. This I accomplish as follows: In Figs. 3 and 4 16, 16 are upright arms carrying a cross brace 15, thereby connecting the two arms 16, Fig. 3. These arms are carried by the shaft 15". 17 is a link connecting arm 16 with lever 18. There are two of these links in practice and two of these levers 18. 19 is also an arm. These two arms are pivotally supported on the shaft- 8. 20 is also a link. 21 a looking bell crank lever carried by the shaft 22.

As shown in the solid drawing in Fig. 4, the packers are raised and the lid is over the top of the compression chamber. It will be seen the link 6 has a slotted end 23 in which slot the stud 24 plays, the latter being fixed to the arm 7. Now as the arm 7 oscillates machineward the link 6 will slip in the slot until the pin 24 contacts with the other extremity of the slot. During this motion of the link the lid is motionless: Thus the angular motion of the arm 7 between the radial lines 26 and 27 operates the lid of the compression chamber: \Vhile the arm 7 moves from the radial lines 25 to 26 the arm 19 moves from 28 to 29 and at this same time the link 20 is raised by the lever 19 and the pin 31 of the bell crank 21 is in contact with the lower end of the slot 32. The lid is now commencing to move and the bell crank 21 is also commencing to move. It will be seen thereafter as the arm 7 has moved the lid from the path of the plates U they will drop down into their respective compartments in the compression chamber, as shown by the dotted line 34. As the shaft 14, which carries the cam 13 is in continuous rotation it will raise and lower the lever 11 until the chambers are full or until it is thrown out of the line of contact with the periphery of the rotating cams which actuate the levers 11.

In practice the compartments are filled before the lid returns and then the meal will hold them out of the path of the returning lid. It is only necessary to raise the lever 11 a few times and to drop them a like number of times until the compartments and the chamber are filled as tight as good work in oil expressing requires. To prevent the possibility of accident, however, it is necessary to force the levers up independent of the condition of the packed meal in the com partments of the compression chamber. This I accomplish as follows: The link 17 carried by the arm 18 at its upper extremity carries a slotted portion 85. When the levers 16 are in the position indicated by the dotted line 34 the upper portion of this slot 36 is in contact with the pin 37 and the arm 18 is in the posit-ion radially relative to the arm 19 indicated by the dotted line 38. But as the arms 7,19 and 18 are all rigid with the same shaft, as the lid closes the pin 37 is engaged by the link 17 and the arms 16 are raised, and as the bar 15 which connects these two arms is of course actuated by them and contacts on the under side of the levers 11 the said levers 11 are thus raised and with them the plates U and the packers V,

and after they are so raised the bell crank 21 is again oscillated from the position indicated by the dotted line, Fig. 4, where it remains while the arms 16 are down to that position shown in the solid drawing, as shown in Fig. 4. Thus are the levers 11 locked and held up out of the path of the lid F until it is again moved from the top of the compression chamber in the manner hereinbefore described.

It is hardly necessary to say that the packing of the compartments is accomplished while the lever 7 is traversing the angular movement equal to the distance of the slot 23 on its return motion.

At this point and in this connection it may be well to describe how. I start the operation of my machine. In Fig. 4 39 is a hand controlled movable plate separating the meal warmer from the meal heater. Of course these two chambers really constitute a heating chamber, but for the purpose of the efliciency in work it is necessary to separate these chambers by the partition 39, for the following reasons: As already stated in this specification seed meal must be hot to extract the oil effectually. The plate 39 holds the meal in the chamber 1 for a period of 30 minutes for cotton seed meal and 50 minutes for flaxseed meal thereby cooking it. The chambers must be brought to the proper temperature to do this. After it is properly cooked I withdraw the plate 30 and allow the meal so cooked to fall into the chamber H. This, as I already explained I term the warming chamber and its temperature is lower than that of the cooking chamber above. I then allow the meal to remain in the warming chamber until a second lot of meal is cooked in the cooking chamber, then the machine is ready for its daily work. Vhile the above cooking and heating are in progress the compression chamber and all the compartments thereof have become heated to the proper degree to facilitate oil flowing and extraction and as the machine starts this chamber 1 by the opening of the lid as described receives the meal thus discharged therein. The meal is carried first to the bin J, thence to heater a, thence to warmer H from which it is discharged to the compression chamber 1, from which the oil flows to the collector IV and pipe E in the direction of the arrow to the oil reservoir. As the chamber is emptied after each pressing the residuum is carried away by belt 39 in the direction of the arrow shown in Fig. 4 to any common receptacle which may await it.

40 is the holder of the lateral plates I which form the walls of the compression chamber and 41 are screws carried thereby receiving the stress on these plates. There can be any number of these holders. They are the same as shown in my former applications, for a like function and I do not show them except in Fig. 4.

K is a shaft.

r is a fan carrier arm and S S are a series of meal agitating arms carried by the said arm. These meal agitators are in continuous motion during the operation of the machine. The shaft M carries the gear N and the shaft K the gear L.

P is a fast and O is a loose pulley actuated by the prime shaft of the pressing room, not shown.

After the chamber formed by the lateral plates I, I is filled in the manner hereinbefore described, and the mechanism started the accumulator 42 forces the water through the pipe 43 into the valve chamber 44 and then through the pipe 45 into the chamber 46 of the cylinder A. The valve 47 must be open when the machine is in operation normally, but this valve is controlled by the machine automatically. 48 is also a valve. This valve at the end of a days operation is closed. I would note that when the valve 48 is open it is equivalent to the operation of the pump, for when the pump stops the pressure ceases, so when this valve is closed the means for producing pressure is not in action. Now as the valve chamber 44 is connected with the small hydraulic chamber 50 by the pipe 160, Fig. 1, the pressure in this chamber is the same as the pressure in the pipe 45 and the same as is the pressure in the cylinder A, therefore, when the pressure is sufficiently great to raise the lever 54, which is carried by the piston 51 of the chamber 50, the valve 47, through the link 67 will be closed closing the pressure at a fixed maximum. This maximum in the machine shown in Fig. l is at 3000 pounds pressure per square inch. Simultaneously with this movement the belt from the line shaft of the oil mill, not shown, will be moved from the loose pulley 56 to the fast pulley 57 and this fast pulley will then rotate the worm wheel 58 and through the shaft 69 and pinion 70 the rack 68 will be moved. This is best shown in Figs. 7, 11 and 1. The trip and time indicator 60 is moved by the rack 68 but not carried by it. Therefore the trip is moved toward the lever 40 which it trips whenever the hydraulic cylinder belt is on the pulley 57 and this always happens when the valve 47 is closed.

The manner in which the trip is supported to move with the rack is as follows: 71, 71 are two supports for rods 52 and 53. These rods are fixed to these supports. 72, Figs. 1, 7 and 10, is an arm fixed to -the frame of the machine and is the guide for the rod 53 as well as for the carrier 71 and the trip 60', and the rack 68 is part of this fixed combination, it being carried by the part 71, best shown in Figs. 10 and 12. It, therefore, follows that the moving of the rack will move the trip 60. Now when I set my trip to an indicated numeral that indicates that the trip will consume that number of minutes until it moves the lock holding the exhaust port and high pressure is held during this time in the cylinder A. The moment pressure would slack for any cause the piston 51 in the accumulator will drop and, therefore, the weighted lever 54 will also drop and the valve 47 be thereby opened. Now again the pressure from the accumulator will force the pressure in the cylinder A up to the indicated high pressure, 2'. 0., 3000 lbs. per

square inch. Whenever the valve 47 is closed and the high maximum pressure is in the cylinder the trip stops because the belt is on the loose pulley and the shaft 59 will not rotate, but whenever the pressure is at maximum the belt is on the fast pulley and the trip and time indicator is moving toward its tripping point, i. e. the valve locking lever .46. l/Vhile this time recording and pressure sustaining mechanism, as shown in Fig. l is shown as interposed between the accumulator 42 and the cylinder A, and, in being so interposed I operate a valve 47 to shut off my means for producing pressure in the cylinder, yet I could employ the same device when I operate directly from a pump to the said cylinder A. In this latter case, however, I would dispense with the valve 47 and merely shift the belt of the pump by substantially the same means I employ in Fig. l.

I have now described how I sustain the pressure, how I predetermine a time period for sustained maximum pressure and during which period a fall in pressure below the normal maximum will not count against this time period for maximum pressure. The manner in which I adjust my trip for maximum pressure sustaining is as follows: I free the screw 74 from its rod 53, this releases the trip 60, and then I slide the trip to the desired time indicated by the indicator plate 51. This I can vary from 1 to 15 minutes on the indicator as shown in Fig. 7 and l to 18 minutes as shown in Fig. l and whenever I stop my trip and fix it to the rod 53 by the screw 74 the time so indicated is the period for sustaining maximum pressure.

When presses are actuated from an accumulator the pressure is high and constant and greater than the desired maximum.

Therefore before I exhaust the water from the hydraulic cylinder it is necessary to keep the valve 47 closed and not to open it until the lid of the compression chamber is opened and about closed. The reason for this is obvious. For otherwise the accumulator would discharge its reserve pressure, or the water which gives it its reserve pressure, directly through the exhaust port. This condition does not, however, exist where the pump pumps directly into the cylinder of the press. Because the action of the pump would merely throw the water it actuates at each pulsation through the said exhaust port with little waste of energy. I accomplish the above desired result as follows: 67 is a link pivoted to the weighted lever 54. This lever, as explained, controls the valve 47. Now the lever 54 is liable to oscillate and open and close the valve 47 by the means already described, thereby feeding water to the cylinder A, when pressure drops and it will close it off when pressure is up. It will do this during the period of high pressure sustaining if there is any leak in any part of the connections, and it is rare that there is not some leaking in high pressure hydraulic devices. But when the period of high pressure, as predetermined by the indicator 60, has expired and this trip 60 contacts with the lever 46 and oscillates it to the position shown by the dotted line 17 6, Fig. 7, the weight 62, through the chain 77, will swing the valve operating disk 45 to the position shown by the circumferential line 78, Fig. 7; and as the valve 79, shown in section, Fig. 8, is carried by the disk 45 it will be moved 90 and the port 80 will thus be opened. This will allow the Water to flow from the chamber A. It is evident that the trip 60 will only move when the pressure is at maximum, because it can only move when the rack is moving and the rack 68 can only move when the belt shifter 55 holds the belt on the fast pulley 57. Therefore the valve 47 is always closed when the belt is on the fast pulley. Now as the weight indicating arm is raised by the accumulator piston 57 through the pin 81 on the said arm and is held up only at maximum pressure, the instant the exhaust port 80 is open it would drop and thus permit the water in the accumulator to be discharged. I prevent this by the following means: shown only in Fig. l. 82 is a bell crank lever cam shaped and adapted to swing in the vertical oscillating path of the weighted lever 65. 83 is a chain carried by the disk locking lever 46 and instantly the said lever is oscillated the said cam is thrown into a vertical position and in the path of the lever 65 and the said lever 65 cannot now drop.

The dotted line 82 Fig. 1, shows the locking position of this locking lever. This keeps the valve 47 closed because the lever 54 cannot drop and the link 67 cannot perform its valve unlocking functions. parts remain in this position until the compression chamber is emptied, trays cleaned and the compression chamber filled again, after which, as the lid F is closed, it operates the lever 84, Fig. l, and through the chain or link 85 returns the bell crank 82 to its normal position, permitting the levers 65 and 54 to return to their normal positions, thus opening the valve 47 and permitting the water to flow from the accumulator 42 to the cylinder A in the manner hereinbefore described. Simultaneously with the unlocking of the bell crank 82 the disk 45 is reseated back to normal by the link 86 connected with the lever 84 at the .one end and with one of the arms of the said disk at the other. The exhaust port 80 is thus closed and the valve 79 reseated. This is best shown in Figs. 1, 7 and 8. The pressure is now again on the cylinder A. The dotted lines 87 and 88 represent the The pression chamber; how I start the compression, how I predetermine the pressure, how I hold the pressure at a predetermined maximum regardless of falling pressure by possible leakage of connections, how the water is automatically exhausted, how the accumulator is locked against feeding water to,

or wasting it through the exhaust port and how the mechanism is automatically thrown into operation at conclusion of the filling of the compression chamber.

I will now describe how I disengage the rack 68 from the action of the fast pulley the moment the water is exhausted as described. This is bent shown in Figs. 7 and 42, also 1. 69 is a shaft fixed to the worm gear. 49is a clutch having an annular channel 89 in which is carried a clutch actuating pin 48. 90 is a secondary shaft supported on a bearing 91 at its lower end and at its upper end held to the clutch member 49. which has a hole forming a bearing therefor. 93 is a hole in the clutch jaw 94 and 92 is a pin carried by the clutch 49 which looks in the hole aforesaid. There can be a number of these holes. 95 is a pin carried by the disk 45 and 61 is a lever supported on a fixed part 96. As the disk 45 is thrown by the weight 62 after being unlocked by the trip 60 contacting with the bell crank disk retainer 46, the pin 95, being rigid with the disk 45 will oscillate 90 in the are shown at 98, Fig. 7. This will oscillate the arm 61 from the radial line 99 to the radial line 100 and the rod 97 will be raised from line 102 to the line 101, Fig. 7. Now as the lug 48 is carried by this rod and the said lug engages with the annular channel in the clutch 49 the clutch jaw will be immediately disengaged from the jaw 94 by withdrawing the pin 92 from the hole 93. The shaft 90 will then stop regardless of the continued motion of the shaft 69 and as the pinion 70 is fixed to the shaft 90 and rack 68. which actuates trip 60 is operated by the said pinion this trip will stop. In Fig. 7 I show a sectional view of a lug 103 carried by the stop 60 on its arm 47. This trip is on the horizontal plane of the angular lug 105 of the disk 45 and will force the unseating of the valve 79, thus insuring the opening of the port 80.

vulcanized fiber.

4, 4, 4, 4, 4 are a series of drainage racks and compartment partitions of this chamber. These racks are subject to heavy lateral pressure, as much as 2000 pounds per square inch at times. It is necessary that the drainage elements should remain intact during this enormous pressure. I therefore construct the racks in the following manner. Fig. 24, 106 is a heavy mesh wire cloth. This forms the oil conducting or drainage element of the partition. As shown in Fig. 23 this member is in the center of the rack. 107, Fig. 25, is a perforated metallic sheet. It could be made of steel, copper or flexible The perforations are about of an inch in diameter. Fig. 26 shows a very fine woven wire cloth, as fine as the finest camels hair cloth. 27 is a very heavy cotton fabric about of an inch in thickness. This is the percolating element of the combination. Fig. 23 shows the manner of combining these elements into the complete drainage member. 106 is in the center. Next on either side are the plates described 107. On the outer side of these plates there are the fine wire sieves 108. On the outer side of these plates is the percolating cloth 109: they are all bound by clamps 110, shown in section in Fig. 23. These parts are all held to a top metallic strip shown in Fig. 31. In Fig. 5 I do not show the elements of the compartments as space forbids, likewise in Fig. 6.

lVe will now assume that the compression chamber has all its compartments filled and the lid of the chamber is closed. The platen 3 is then forced up as already described. Each of the racks carries a top cap or plate 112, Fig. 31 only. 111 is a lug one each of the racks. These lugs carry links, cam shaped links 113. These links while the chamber is filling are taut, as shown in F 5 and 6, but as the pressure of the platen 3 forces the chambers together the distance be tween the racks becomes smaller and smaller and the cam links gradually intertwine and contract their centers asshown in Fig. 32 until the predetermined limit'of pressure is reached. WVhen this is accomplished the exhaust port 80 is opened through the valve 79 on the disk 45, and the weight 87 through the chain 88' will pull back the platen 3.

114 is a cam faced angle plate carried by I the platen.

115 is a sliding bar, or cross bar having spring retaining lugs 123 and 123 on either side. These springs are four in number, one for each corner of the end compartment contacting with the platen.

117, 117 are two lugs cam shaped on their platen end. The bar 115 is also cam shaped on its end or wall facing these lugs.

116, 116 are lateral bars extending the width of the compression chamber. They are connected at their platen end with the bars 117. There are two of these bars 117, one on the upper and one on the lower side of the ram. These bars have cam shaped recesses at their platen end and into these recesses the sliding bar 115 fits. At the other end these four bars are all held to the compartment which rests against the head of the compression chamber 10. Now as the platen is forced back after pressure has been up to maximum the angular member 114 will engage the sliding bar 115 and force .it into the aforenamed cam shaped recess of the bars 116 and the angle plate 114 will then pass over it and lock it in these notches. The springs 124 are of such strength that they will pull the compartments with but little yielding in their or during their reciprocating movements. So when the bar 115 is locked to the four bars 116 I have a rigid frame with the drainage compartment 4 at one end and forming the end thereof and the drainage member 4 at the other and forming the opposite end thereof. The series of cam links already named 113, 113, 113, 113, connecting these two ends and on these links are suspended the drainage partitions 4, 4, 4, 4, with all their elements as already described. The two ends, it will be remembered. are supported on the bars 116. These partitions fit snugly the lateral walls, the top and the bottom of the compression chamber and to clean them from residuum I reciprocate them longitudinally in the compression chamber. The trays or drainage partitions are thus all looked to the four bars 116, 116, 116, 116, and thus as the cross bar 126 is a link connecting the arm 119 of the bell crank lever with the rod 129 and the latter rod is operated by the eccentric 130, shown only in Fig. 3. This eccentric is carried by the shaft 131 and this shaft is rotated fast or slow depending upon the gear with which the clutches 135 or 135 is in operative contact. The clutch 135 operates gear 132 for the slow reciprocation of the racks and the clutch 135 operates the gear 133 for the fast reciprocation of the said racks. These gears are the prime movers for the clutches as shown in Fig. 1 and Figs. 3 and 2. In Fig. 2 I show the gears by dotted pitch diameters. The gear 132 is actuated by the gear 134 for slow speed for shaft 131. The gear 133 actuates gear 135 for high speed for shaft 131. The clutches are so adjusted and the machine so timed that the slow speed is in action when the trays are first moved and after a limited motion at this speed the cam 136 throws the clutch into the high speed, which reciprocates the racks rapidly. The reciprocation of the racks takes place while the lid of the chamber is closed and the bottom is open.

137 is a clutch operating arm and 138 a crank carried by shaft 141. 139 is a link operating lever 140 and 142 is an arm carrying link 143 for operating oil collector IV. 145 is a shaft carrying crank 144 and 146 is a link connecting this shaft with crank arm 147 and 147 is carried by shaft 148. In practice I prefer two arms 7 and two arms 1 42, as shown in Fig. 3, though but one is shown in the drawings. These parts are all old and are shown in my applica tions hereinbefore referred to. for engaging the clutches on the return of the platen is also old being shown in the same applications and I do not therefore deem. it of importance to give such a full and detail description here, as otherwise would be necessary. Suflice it to say that as the platen returns it strikes the lever 162, Fig. 3, and the link 163, through the friction roller 164 forces the clutch 165 in engagement with the clutch 166, whereupon the shaft 141 is rotated. The rotation of this shaft opens and closes the bottom of the compression chamber W. The elements engaged to do this are the crank 138, the link 139, crank 140, shaft 159, arm 142 and link 143. As the shaft 141 makes one complete rotation the rod 167, shown only in dotted line, Fig. 3, engages the end of the arm 163 and oscillates it to disengagement from its lock, not shown because old as above. Then the spring 168 forces the clutches 166 and 165 apart and the arm 169 forces the clutches 170 and 171 together, thereupon the shaft 145 is actuated by the gear 157 and also the gear 158 and the operation of this shaft rotates crank 144, which through link 146, Fig. 2, operates lever 147 shaft 148, arms 18 and 19, lever 7 and link 6 all for the purposes already fully described. After a complete rotation of the shaft 145 and a return of all these elements to their respective normal positions the clutch jaws 170 and 171 are unlocked and the mechanism comes to rest. The unlocking of these elements is old in the applications hereinbefore referred to.

In Fig. 28 I show a series of hydraulic cylinders A, A, 1 operated by a common accumulator. This arrangement of presses would be used where a common accumulator feeds water to presses instead of an individual pump for each press. The object is to vary the pressure in the presses automatically regardless of the pressure in the accumulator. The pressure when varied is to be considered at maximum. In the time recorder and pressure sustaining device I only show the exhaust valve disk 45 and The means 1, 7, 9, 10 and 11 and considering the lack of ample space on the sheet a repetition of the other elements is deemed needless.

42 is an accumulatorreceiving Water from the pump 180 through the pipe 49.

A is a small hydraulic cylinder, A is a large hydraulic cylinder and A is an intermediate cylinder. Now the pressure in pipes 175, 177 and 178 is uniform but the pressure in all the cylinders at the same time is liable to vary and will vary where they are not the same size, allowing that they receive water from the same accumuator. If I desire to predetermine my maximum at a different degree of pressure I can do so entirely independent of the pressure in the pipe 175. This is a very essen' tial feature in an automatic oil mill. In fact no matter how many presses are in operation from the same accumulator this feature insures the entire oil mill being entirely automatic. If for any reason I wished to have the time on some of the presses 'short at high pressure and others long sustained the individuality of all the presses of the series, and their absolute independence, each of all the others, will enable me to do this.

182 is an outlet pipe from the cylinder A leading to the exhaust chamber 183.

184 is an outlet from the exhaust chamber leading to the hydraulic accumulator 185. This accumulator performs the same function as does the accumulator 50, Figs. 1 and 11 and it is in fact the same accumulator differing only in position. The numbers, as deslgnating these elements, are changed as a matter of convenience in description. They are to be considered as one and the same elements. There is no difference in any of the co-acting elements of these chambers.

186 is a weight to reseat the ram 187 after the exhaust disk 45 has opened the valve as shown in Fig. 8.

190' is a valve operated by the ram 187 through the link 191. When pressure is applied and is up at maximum the arm inclicated by the dotted line 189 will have moved to dotted line 188. This closes the water ofi of the chamber A. If leakage should occur the pressure would sink below normal and the weight 186 will open valve 190 and keep it open until the pressure is again forced up as described. This mechanism is substantially the same as shown in Fig. 1.

It will be apparent that the pressure in any one of the series of cylinders, A, A, A, is not up to maximum, as predeterminable by the means shown in Figs. 7 and 1, until the pressure in the chambers 183, 183, 183" is up to this predetermined maximum. And this chamber 183, it will be remembered, is the same as chamber 44, the exhaust chamber. Therefore, as soon as the pressure is at maximum the valve 190, as indicated in Fig. 28, which, be it remembered, is the same as valve 47, shown in Fig. 1, will be closed. On fall of pressure below the predetermined maximum it will be opened, as I have already described. Therefore I control the pressure in the cylinders entirely independently but each through its individual cylinder. The pump 180 keeps the accumulator up and the accumulator, through the conductors 175, 178 and 176 177 feeding the water or liquid to the difierent cylinders, and the cylinders through conductors respectively 181, 179 and 182 feeding the exhaust ports in chambers 183 183 183, Fig. 28, and the exhaust chamber feeding the accumulator 185, and the ram 187 of this accumulator controlling the valve 190 through the link 1 91. The weight 194 is shown as a means to open the exhaust ports after unlocking, as already described, and as illustrated in Figs. 1 and 7 and other views. I

Fig. 9 shows a modified way of connecting the valve actuating means with the accumulator 50. The link 67 swings the valve lever 198 from line 199 to line 200 as the arm'54 is raised to line 197 meanwhile the integral arm 201 will be oscillated from line 195 to line 196. The function of this modified mechanism is the same as that shown in Figs. 1 and 28.

I desire it distinctly understood that I consider the accumulator 42 as the full equivalent of the pump 180 and that the closing and the opening of the valve 190, Fig. 28 or 47 Fig. 1, is the equivalent of the shifting of the belt from the fast to the loose pulley of a pump. In each case I start or arrest increasing pressure in the compression chamber, and specific modifications to this end are not at all material.

Figs. 29 and 30 also Fig. 1, show an automatic belt shifting device. a and a are two tight pulleys carried by the prime shaft 15 of the machine. They are operated directly by the line shaft of the pressing room, not shown. The bell crank lever 200 through the link 201 actuates the belt shifting fingers 205 and 206. 207 is a cam. 208 is a cam faced bar. The cam 207 is provided with a means to pivotally support it to the shifter 204. A stop 210 prevents the cam from falling from its normal position as shown in Fig. 30. 211 is a stop lug carried by guiding rods therefor 212 and 213, controlled by springs 214 and 215. This lug carries the belt actuating fingers O and C. The object of the mechanism described is to reverse the shaft 15" in order to relieve the contact clutch pins 7) and b from the enormous friction existing by their contact and thus to insure that the spring 168 will force the said clutch jaws apart. This occurs in the shifting of the power from the bottom actuating mechanism to the top or lid actuating mechanism through I the shifting of the belt which I accomplish as follows: The arm 200 is raised by the spur gear 158 and immediately on so being raised the link 201 moves the belt moving finger 205 from the wheel a to the wheel a shifting the belt held by the fingers from the fast pulley 64" to the loose pulley a. This will rotate the prime shaft of the machine 15 in its normal direction for work, but while this movement is in progress, and near its inception, the part 211 engages the stop therefor 216 and arrests its motion, the supporting rods 212 and 21,3 slide thereafter in their guides compressing the springs 214 and 215, thereby storing energy to shift the belt controlled by the fingers C and C" as soon as the cam 207 contacts with the cam face 208, the effect of which contact is to raise the part 211 and thus disengage it from the stop 216. Immediately on the part just described being so raised the springs aforesaid will be free to exert the energy their compressed condition gives them and the finger C will, by virtue of this energy. exerted, force the belt from wheel a to wheel a, thus reversing the prime shaft 15. It will be seen that the part 211, Figs. 29 and 30 rests on the cam arm 207 and thus moves up with the said arm. It will also be seen that the head of the said cam arm hooks around the said finger carrying arm or part 211 and thus the return of the belt shifter 204 to normal also returns the fingers C and C to normal. The arms 0, e are the supports and guides for the spring controlled rods 212 and 213 and they are carried by the cam piece 207.

I have described how I shift the belt from the normal rotating to the reverse rotating pulley, for the pulley a", it will be understood, carries a twisted belt and this belt is normally on the loose pulley. The shifting of the belt to the fast pulley is but for a moment, as the instant the pins 6 and 5 are frictionally released the spring 168, Fig. 3, disengages the said clutches. I will now describe how the belt shifter is actuated and how the same is reseated. The gear 155 is fixed to the shaft 14 as already described, and the clutch 165 is splined to this shaft, as also explained. The clutch pin holder 212 of the shaft 141 is normally disengaged from the clutch pin holder 166: Therefore, the shaft 141 can rotate only when the pins 5 and 5 are engaged with the pins carried by the parts 212, or pins 5 and b. After the platen has engaged the pins aforenamed carried by the pin holders 212 and 166 through the lever 162 and link 163, Fig. 3 only, the pins aforenamed become locked together or are held in the same vertical rotary plane. Now as the shaft 14 and the gear 155 rotate the shaft also rotates.

225 is a lever pivoted at 226, Fig. 37. This lever carries a cam faced projection 227 and this projection is in the rotary path of the pawl or dog 228, best shown in Fig. 38. Now as the said dog strikes the said cam of the said lever 225 the lever is oscillated from the position shown in the solid drawing, Fig. 37, to the dotted line 229. The oscillation of this lever will move the lever 200 from the position shown inthe solid drawing, Fig. 37, to the position shown by the dotted line 230. This will slide the aim 202, which carries the belt shifter support 204 from the line 231 to the line 232, Fig. 37, and move the belt from the wheel a to the wheel a; and also, in the manner already described, and as shown in Fig. 30, the belt from the loose pulley a to the fast pulley a. Now by consulting Fig. 39 the belt 233, which is the belt 011 wheel a, is a twisted belt, as already hereinbefore stated, and gives to this pulley, therefore, a reverse motion to that given by the belt 234, which is the belt carried by the wheel 64". Now as the shaft 15, which carries the wheels 64", a', a and a is the prime shaft of the machine, and all the other ele ments are controlled by its motion, the effect of this reverse motion is to free the pins 5 and 5 from the pins 5 and Z) and immediately the spring 168 will force the pin holders 212 and 166 apart, as already referred to, and after so forcing them apart it will also force the clutch gear 157 in engagement with the clutch pin holder 170. Now the gear 157 is mounted loosely on the shaft 14 and rotates, therefore, independent of the rotary motion of the shaft and the clutch pin holder, it will be remembered is keyed to the said shaft 14 therefore the gear 157 will rotate in its now shaft locked position. The rotation of this gear rotates the gear 158 and this gear operates the compression chamber lid F, as already described. 236 is a stud or pin carried by the gear 158.

The manner of unlocking the clutch pin holders 170 and 157 is as follows: as the gear 158, nears the end of its rotation, it strikes the pawl 237 of the arm 238 integral with the arm 200. It will then oscillate this arm from the position shown in the solid drawing, Fig. 37, to that indicated by the dotted line 239 and the effect of this oscillation will be the same as that formerly descrlbed: 2'. e. to move the arm 203 carrying the belt shifter 204 from the line 231 to the line 232 and the belts 233 and 234 will act as before reversing the belt wheel with the reverse or twisted belt and so changing the rotation of the shaft 15 and freeing pins 171 from pins 240.

241 is a locking dog for the clutch and as the spring 168 forces the jaw up the said dog will snap into the position shown in 

